WO1998047981A1 - Quench cooler - Google Patents
Quench cooler Download PDFInfo
- Publication number
- WO1998047981A1 WO1998047981A1 PCT/US1998/004900 US9804900W WO9847981A1 WO 1998047981 A1 WO1998047981 A1 WO 1998047981A1 US 9804900 W US9804900 W US 9804900W WO 9847981 A1 WO9847981 A1 WO 9847981A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- tubes
- section
- connecting means
- quench cooler
- passage
- Prior art date
Links
Classifications
-
- C—CHEMISTRY; METALLURGY
- C10—PETROLEUM, GAS OR COKE INDUSTRIES; TECHNICAL GASES CONTAINING CARBON MONOXIDE; FUELS; LUBRICANTS; PEAT
- C10G—CRACKING HYDROCARBON OILS; PRODUCTION OF LIQUID HYDROCARBON MIXTURES, e.g. BY DESTRUCTIVE HYDROGENATION, OLIGOMERISATION, POLYMERISATION; RECOVERY OF HYDROCARBON OILS FROM OIL-SHALE, OIL-SAND, OR GASES; REFINING MIXTURES MAINLY CONSISTING OF HYDROCARBONS; REFORMING OF NAPHTHA; MINERAL WAXES
- C10G9/00—Thermal non-catalytic cracking, in the absence of hydrogen, of hydrocarbon oils
- C10G9/002—Cooling of cracked gases
-
- C—CHEMISTRY; METALLURGY
- C10—PETROLEUM, GAS OR COKE INDUSTRIES; TECHNICAL GASES CONTAINING CARBON MONOXIDE; FUELS; LUBRICANTS; PEAT
- C10G—CRACKING HYDROCARBON OILS; PRODUCTION OF LIQUID HYDROCARBON MIXTURES, e.g. BY DESTRUCTIVE HYDROGENATION, OLIGOMERISATION, POLYMERISATION; RECOVERY OF HYDROCARBON OILS FROM OIL-SHALE, OIL-SAND, OR GASES; REFINING MIXTURES MAINLY CONSISTING OF HYDROCARBONS; REFORMING OF NAPHTHA; MINERAL WAXES
- C10G9/00—Thermal non-catalytic cracking, in the absence of hydrogen, of hydrocarbon oils
- C10G9/14—Thermal non-catalytic cracking, in the absence of hydrogen, of hydrocarbon oils in pipes or coils with or without auxiliary means, e.g. digesters, soaking drums, expansion means
- C10G9/18—Apparatus
- C10G9/20—Tube furnaces
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
- F28D7/10—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically
- F28D7/106—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically consisting of two coaxial conduits or modules of two coaxial conduits
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
- F28F9/02—Header boxes; End plates
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
- F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
- F28D2021/0075—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for syngas or cracked gas cooling systems
Definitions
- This invention relates to a novel heat exchanger or quench cooler for quenching the effluent from a hydrocarbon cracking furnace. More particularly, the invention relates to the coupling between the cracking furnace tubes and the tubes of the quench cooler or transferline exchanger.
- quench cooler designs are available in the marketplace depending upon the quantity of cracked gas to be cooled, the fouling tendencies of the furnace effluent and the pressure/temperature conditions of the steam to be generated. These designs range from conventional fixed tubesheet shell and tube heat exchangers to double pipe designs.
- the cross sectional area for flow through the connector is substantially uniform to achieve substantially constant gas velocity throughout the distributor.
- the distributor may also be divergent in cross sectional area up to the point where the ratio of the sum of the cross sectional areas of the branches to the cross sectional area of the inlet is 2: 1.
- the inlet section or connector for a quench cooler between the furnace outlet and the inlets to the quench cooler tubes splits the flow into a plurality of branches and is designed to reduce the inlet section residence time to a minimum.
- the flow passages are configured to first efficiently decelerate the gas leaving the furnace and then re-accelerate the gas to the quencher cooling tube velocity.
- a conical diverging diffuser section in the connector decelerates the gases and then a tapered and branched converging section re-accelerates the gases as they are fed into the quench cooler tubes.
- the cross sectional transitions are smooth with monotonic area change in the flow direction (aerodynamic) so that dynamic pressure is recovered, dead spaces, i.e. zones of flow separation, are avoided and the pressure loss is minimal.
- the present invention relates to the inlet section or connector for a quench cooler between the furnace outlet and the inlets to the quench cooler tubes.
- the quench cooler makes use of the double tube arrangement with an oval header for the outside tubes and with the plurality of quench tubes being arranged in a circular fashion.
- the connector provides a conical diffuser channel which decelerates the gases leaving the furnace and then provides a radial diffuser to direct the gases outwardly. The connector then provides for the smooth re- acceleration of the gases into the circular arrangement of cooling tubes at the working tube velocity.
- Figure 1 shows a side elevation view of a quench cooler partially in cross-section incorporating the present invention.
- Figure 2 is a cross-sectional view of the quench cooler of Figure 1 taken along line 2-2.
- Figure 3 is a perspective view of the connection of the tubes to and through the oval header.
- Figure 4 is a cross-section view of the outer section of the connector.
- Figure 5 is a cross-section view of the inner section of the connector.
- Figure 6 is a top view of the inner section of the connector taken along line 6-6 of Figure 5.
- Figure 7 is a vertical cross-section view of a portion of the connector section of Figure 5 taken along line 7-7. DESCRIPTION OF THE PREFERRED EMBODIMENT
- the quench cooler 10 comprises a plurality of double tube heat exchange elements 12 which in turn comprise the inner tubes 14 which carry the cracking furnace effluent gas surrounded by the outer tubes 16.
- the annulus between the two tubes carries the coolant water/steam mixture.
- the lower ends of the tubes 14 and 16 are connected to the oval header 18 while the upper ends are connected to a similar oval header.
- the connection of the tubes to the oval headers is shown in detail in Figure 3.
- the inner tubes 14 pass completely through the header while the outer tubes 16 terminate at the header and are open to the inside of the header.
- Cooling water which is supplied to the lower header 18 via the coolant inlet header 20 and the radial coolant tubes 22, as shown in Figure 1, flows through the lower header 18, into the annular space between the tubes and upwardly emptying into the upper header.
- the coolant which is now a heated steam/water mixture, flows out from the upper header into the coolant outlet header 24.
- the cooled gas which is flowing up through the pipes 14, empties into the upper outlet chamber 26 and is discharged through the outlet 28.
- the present invention is illustrated using an 18-tube arrangement which is best seen in Figure 2.
- This figure shows the annular oval header 18 to which the elements 12 are connected.
- a plurality of the water inlet connections 22 are shown extending between the header 20 and the header 18.
- the water inlet to the header 20 is shown at 21.
- the quench cooler of the present invention can be applied most advantageously with cracking furnaces (not illustrated) employing a relatively small number of high capacity cracking coils.
- such a furnace might have six coils each 12 meters (40 feet) in height with each coil formed from a multiplicity of inlet tubes feeding into a single 16.5 cm (6.5 in.) internal diameter outlet tube.
- the effluent from one such coil can be quenched in a single quench cooler of the present invention.
- the quench cooler typically has sixteen or more quencher tubes.
- the connecter 30 at the lower end of the quench cooler comprises a container 32 which forms the pressure boundary.
- a flange 34 around the edge of the container 32 is attached to the flange 36.
- the container 32 houses the components of the present invention which distribute the gases to the circular arrangement of tubes 14 and which provides the diffuser channels to decelerate and then accelerate the gases.
- the lower portion of outside section 38 comprises an outwardly tapered conical diffuser region 42 such that the flow area increases and such that the upwardly flowing gases decelerate.
- the upper portion 44 of the section 38 cooperates with the section 40 to provide radial diffuser and accelerator regions.
- the section 40 is mounted on and extends down inside of the section 38 so as to form the flow passages.
- the sections 38 and 40 are preferably formed from a hard ceramic such as fired alumina but could also be formed from other materials such as high alloy metal castings.
- annular ring portion 46 Located around the periphery of the section 40.
- a plurality of holes 48 extend through this ring portion 46, one hole 48 for each tube 14.
- the holes 48 are located so as to be aligned with the tubes 14.
- the lower, outside surface 50 of the ring portion 46 engages the upper surface 52 of the section 38.
- There is a soft gasket between these two parts which allows for thermal expansion.
- the two sections 38 and 40 are located in the container 32 as shown in Figure 1 and then surrounded by the insulating castable refractory material 54 which fills the space between the sections 38 and 40 and the container 32.
- the gas passage comprises a diverging conical diffuser portion 56 followed by a radial diffuser section 57 which further increases the flow area.
- the height of the radial cross-sectional area of the radial diffuser section may not increase very much and in fact may decrease slightly, the circumferential cross-sectional area increases as the section extends out from the center because of the increased circumference.
- These diffuser portions 56 and 57 are then followed by a converging portion 58. The net effect is a smooth or monotonic convergence of the flow area.
- the gases are first decelerated in the conical diffuser 56 and the radial diffuser 57 and then re-accelerated back up to the quencher tube velocity in the annular converging portion 58.
- the smooth re-acceleration serves to avoid flow separation thereby minimizing coke formation in dead zones while providing a uniform flow distribution to the individual quencher tubes.
- the inside diameter of the inlet tube may be 16.5 cm (6.5 in.) and the inside diameter of the outlet of the diffuser may be 22.0 cm (8.7 in.) for a ratio of flow area of 1.78.
- the flow area then increases further in the radial diffuser giving an overall diffuser area ratio (radial diffuser outlet to conical diffuser inlet of 4.9.
- the flow area then decreases as the gas accelerates into the annulus upstream of the tubes.
- a typical exchanger would have 18 tubes with an inside diameter of 4.8 cm (1.9 in.) giving a flow area 32 percent of that at the radial diffuser outlet. Since the flow is re-accelerated without dead zones, coke deposition at the entrance to each tube is minimized. Even if coke is deposited in the tubes, deviation from uniform flow distribution is significantly reduced. This is the advantage of using an aerodynamically efficient diverging/converging passage instead of a conventional transfer line exchanger inlet.
- the result of applying the diverging/converging passage of the present invention is greatly reduced inlet residence time, uniform distribution, reduced coking tendencies and consequently improved yields and increased run length.
Abstract
Description
Claims
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP54574898A JP3412049B2 (en) | 1997-04-18 | 1998-03-12 | Quench cooler |
EP98911605A EP1009783B1 (en) | 1997-04-18 | 1998-03-12 | Quench cooler |
DE69825167T DE69825167T2 (en) | 1997-04-18 | 1998-03-12 | quench |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US08/844,269 US5816322A (en) | 1997-04-18 | 1997-04-18 | Quench cooler |
US08/844,269 | 1997-04-18 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO1998047981A1 true WO1998047981A1 (en) | 1998-10-29 |
Family
ID=25292259
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/US1998/004900 WO1998047981A1 (en) | 1997-04-18 | 1998-03-12 | Quench cooler |
Country Status (7)
Country | Link |
---|---|
US (1) | US5816322A (en) |
EP (1) | EP1009783B1 (en) |
JP (1) | JP3412049B2 (en) |
KR (1) | KR100319337B1 (en) |
CN (1) | CN1183225C (en) |
DE (1) | DE69825167T2 (en) |
WO (1) | WO1998047981A1 (en) |
Families Citing this family (16)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US6419009B1 (en) * | 1997-08-11 | 2002-07-16 | Christian Thomas Gregory | Radial flow heat exchanger |
DE19833004A1 (en) * | 1998-07-22 | 2000-01-27 | Borsig Gmbh | Heat exchanger for cooling a hot process gas |
US7128136B2 (en) * | 1998-08-10 | 2006-10-31 | Gregory Christian T | Radial flow heat exchanger |
DE19847770A1 (en) * | 1998-10-16 | 2000-04-20 | Borsig Gmbh | Heat exchanger with a connector |
DE10064389A1 (en) * | 2000-12-21 | 2002-06-27 | Borsig Gmbh | Gas inlet hood |
WO2004000767A1 (en) * | 2002-06-19 | 2003-12-31 | Exxonmobil Chemical Patents Inc. | Manufacture of xylenes from reformate |
US7119239B2 (en) * | 2002-06-19 | 2006-10-10 | Exxonmobil Chemical Patents Inc. | Manufacture of xylenes using reformate |
JP5007022B2 (en) * | 2002-06-19 | 2012-08-22 | エクソンモービル・ケミカル・パテンツ・インク | Production of xylene using modified oil |
KR100528167B1 (en) * | 2002-10-24 | 2005-11-15 | (주)우리체인 | Tunnel type catalyst-free waste plastics pyrolysis oil recovery system |
ATE440255T1 (en) * | 2004-05-25 | 2009-09-15 | Shell Int Research | DEVICE FOR COOLING HOT GAS |
EP2154459B1 (en) * | 2006-04-14 | 2018-05-30 | Mitsubishi Denki Kabushiki Kaisha | Heat exchanger and refrigerating air conditioner |
US7802985B2 (en) * | 2007-10-25 | 2010-09-28 | Alan Cross | Direct fired heater utilizing particulates as a heat transfer medium |
CN101769658B (en) * | 2009-12-17 | 2012-12-12 | 中国石油化工股份有限公司 | Fluid distribution method for rapid-cooling heat exchanger |
CN101852556B (en) * | 2010-06-08 | 2012-06-27 | 南京工业大学 | High temperature and high dusty burner gas quencher |
ITUB20150576A1 (en) | 2015-04-24 | 2016-10-24 | Hexsol Italy Srl | HEAT EXCHANGER WITH BUNDLE TUBE AND IMPROVED STRUCTURE |
DE112018008099T5 (en) * | 2018-10-23 | 2021-12-23 | MAHLE Behr India Private Ltd. | Exhaust gas cooler arrangement |
Citations (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO1995032263A1 (en) * | 1994-05-24 | 1995-11-30 | Abb Lummus Global Inc. | Quench cooler |
Family Cites Families (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
NL6514027A (en) * | 1964-12-24 | 1966-06-27 | ||
US4097544A (en) * | 1977-04-25 | 1978-06-27 | Standard Oil Company | System for steam-cracking hydrocarbons and transfer-line exchanger therefor |
DE3842727A1 (en) * | 1988-12-19 | 1990-06-21 | Borsig Gmbh | HEAT EXCHANGER, IN PARTICULAR FOR COOLING FUEL GAS |
-
1997
- 1997-04-18 US US08/844,269 patent/US5816322A/en not_active Expired - Lifetime
-
1998
- 1998-03-12 KR KR1019997009507A patent/KR100319337B1/en not_active IP Right Cessation
- 1998-03-12 EP EP98911605A patent/EP1009783B1/en not_active Expired - Lifetime
- 1998-03-12 DE DE69825167T patent/DE69825167T2/en not_active Expired - Lifetime
- 1998-03-12 CN CNB988040751A patent/CN1183225C/en not_active Expired - Lifetime
- 1998-03-12 WO PCT/US1998/004900 patent/WO1998047981A1/en active IP Right Grant
- 1998-03-12 JP JP54574898A patent/JP3412049B2/en not_active Expired - Fee Related
Patent Citations (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO1995032263A1 (en) * | 1994-05-24 | 1995-11-30 | Abb Lummus Global Inc. | Quench cooler |
Also Published As
Publication number | Publication date |
---|---|
EP1009783B1 (en) | 2004-07-21 |
KR20010006419A (en) | 2001-01-26 |
CN1254362A (en) | 2000-05-24 |
DE69825167D1 (en) | 2004-08-26 |
DE69825167T2 (en) | 2005-07-14 |
EP1009783A1 (en) | 2000-06-21 |
JP3412049B2 (en) | 2003-06-03 |
KR100319337B1 (en) | 2002-01-15 |
US5816322A (en) | 1998-10-06 |
JP2000510519A (en) | 2000-08-15 |
CN1183225C (en) | 2005-01-05 |
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